EP1261806B1 - Inverser verzahnungsrotorsatz - Google Patents

Inverser verzahnungsrotorsatz Download PDF

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Publication number
EP1261806B1
EP1261806B1 EP01907521A EP01907521A EP1261806B1 EP 1261806 B1 EP1261806 B1 EP 1261806B1 EP 01907521 A EP01907521 A EP 01907521A EP 01907521 A EP01907521 A EP 01907521A EP 1261806 B1 EP1261806 B1 EP 1261806B1
Authority
EP
European Patent Office
Prior art keywords
tooth
rotor
toothed
rotor assembly
gearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01907521A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1261806A1 (de
Inventor
Josef Bachmann
Eberhard Ernst
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GKN Sinter Metals GmbH
Original Assignee
GKN Sinter Metals GmbH
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Filing date
Publication date
Application filed by GKN Sinter Metals GmbH filed Critical GKN Sinter Metals GmbH
Publication of EP1261806A1 publication Critical patent/EP1261806A1/de
Application granted granted Critical
Publication of EP1261806B1 publication Critical patent/EP1261806B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member

Definitions

  • the invention relates to a toothed rotor set for a Pump or a motor, which consists of a rotatable outer rotor with in this mounted inner rotor, wherein the inner rotor Has bearing pockets for planetary gears.
  • the gear rotor set is similar to a gerotor pump with toothed Embodiment, wherein the function and mode of operation of the toothed rotor set, which corresponds to a gerotor pump.
  • the pressure chamber from the suction chamber does not separated by a crescent-shaped filler, but a special one Training of the teeth - based on the trochoid toothing - Ensures the seal between-toothed ring and externally toothed pinion.
  • the internal toothed ring has a tooth more than the pinion, so that with appropriate Design of the teeth, the tooth heads exactly opposite touch the tooth engagement point. This ensures unwinding is, must between the tooth head of the external rotor and The head of the inner rotor a head clearance be present.
  • the disadvantage of gerotor pumps is that by this headgear in the gerotor pumps internal leaks and thus a poor volumetric efficiency occurs. hereby can not build up high pressures at low speeds become.
  • the pump forms a Gear rotor set, consisting of a bearing ring with a Internal teeth and an eccentric recorded therein Gear with external toothing, wherein the internal toothing through in the bearing ring rotatably mounted rollers is formed and a Tooth more than the external teeth, wherein the external teeth of the gear fine teeth with a significant smaller module is superimposed and each roll up Their circumference has a fine toothing with the same module, in which engage the teeth of the gear.
  • the function of the toothed rotor set results from that a drive torque via a drive shaft to the inner rotor works and turns this. From the toothed inner rotor becomes a force transmitted to the planet, on the one hand a Impact force through the center of the planetary gear and a circumferential force results, which causes a torque of the planetary gear. Due to the impact force acting on the bearing ring is this set in rotation.
  • the known Veriereungsrotorsatz has the disadvantage that a high number of planet gears must be used to to enable the function and conditioned by the use of high number of planet gears a relatively high proportion of friction consisting of the torque of one with the inner rotor connected drive shaft must be overcome. Further has in the known Veriereungsrotorsatz disadvantageous proved that relative to a rotational movement of the inner rotor in the same direction turning lubricating oil in the tooth gaps of the Planetary gear is conveyed from the pressure side to the suction side, whereby the efficiency of the pump decreases.
  • the results Task to make a gear rotor set that style is that with a similar size a smaller number of Planet wheels used to reduce friction. It is another object of the invention to provide a toothed rotor set to form, which has a higher delivery volume and greater efficiency at comparable size of the known gear rotor set having.
  • a toothed rotor set for a pump or a motor consisting of a rotatable outer rotor, which is an approximately star-shaped Bore with an internal fine toothing and one in the bore eccentrically mounted inner rotor, the storage bags for Having planet gears, the planetary gears have a fine toothing on with you in the fine toothing of the outer rotor unroll, whereby the planetary gears give a toothing, which forms an outer toothing, wherein the outer toothing one tooth less than the internal toothing of the Outer rotor.
  • toothed rotor set designed in this way is that the toothed rotor set according to the invention compared to the prior art known Veriereungsrotorsatz with a smaller number can be operated by planetary gears.
  • less planet gears are used with the same size than in the prior art gear rotor set known in the art,
  • There are fewer friction surfaces such as between the planetary gear and the bearing pocket of the inner rotor, and between the teeth of the planet gear and the teeth of the outer rotor. Due to the lower friction has a pump or a motor with the invention
  • the gear rotor set according to the invention also a larger delivery volume compared to the one from the state The technology known Veriereungsrotorsatz.
  • the toothed rotor set according to the invention has a higher efficiency, as with a rotation of the inner rotor clockwise, the planetary gears rotate in the opposite direction go through and thus additional lubricating oil in the tooth gaps of the planet gears from the suction side to the pressure side is encouraged.
  • Another problem of fine toothing is that the forces and moments occurring in the generic Gear rotor set not optimal by the previously used Involute toothing.
  • the known gearing the shock and Circumferential forces not without large surface pressure in the form of a Line management transfers.
  • the previously known gearing are suitable only for the transmission of high circumferential forces and not for the transmission of large impact forces caused by the Run center of the planetary gear.
  • the outer and / or inner fine toothing at least In some areas of the tooth shape of the toothing an arcuate Share has.
  • the tooth shape in the region of the tooth tip and / or the tooth root Tooth shape is arcuate.
  • the tooth shape in the region of the tooth head and / or the Tooth base makes it possible that very large impact forces (radial forces) be transferred, the proportion of transmitting circumferential force can be low.
  • the tooth head and the tooth base unlike those at Veryakungsrotoren known involute gears in the Rolling process, i. the rolling of the toothed planet wheels on the splined outer rotor curve, with included.
  • the convexly curved tooth flank of the planetary gear and the concave curved tooth flank of the outer rotor form during meshing a relatively large sealing surface, the passage of the Displacement chamber from the suction in the pressure range, the displacement chamber seals. Also deviations of squareness of the rotor do not lead to leakage of the displacement chamber.
  • the region of the tooth head and / or the Tooth base the tooth shape of the fine toothing a flattening having.
  • the Torque through the inner rotor via the toothed planetary gears on the toothed outer rotor acts it comes, geometrically conditionally, almost to a stop of the planetary gear. at the described relative standstill and the simultaneous Transfer of a large force there is a risk that the Lubricating film between the Planetenradtechnikkopf and the bearing pocket of the inner rotor collapses.
  • the planet gear teeth were flattened. The size of the flattening depends on the field of application of the toothed rotor.
  • the tooth shape has a large radius of curvature having.
  • the area of the tooth head and / or tooth root an area with to provide a large radius of curvature.
  • the arcuate portion at least partially is designed as a cycloid.
  • the cycloid has proven to be special advantageous in terms of the rolling behavior and the Transferring the impact forces proved. This cycloid toothing guaranteed even with significant changes in curvature and small radii of curvature ongoing low-friction unrolling, which in turn reduces the wear.
  • the fine toothing has a low-wear surface.
  • the low-wear surface can be replaced by a chemical, in particular thermochemical and / or physical Surface treatment can be achieved.
  • the surface can continue to be galvanized. Further advantageous surface treatment methods are caburation and nitration and / or nitrocarburizing, boriding and / or chromating.
  • At least one fluid channel is arranged in the region of the bearing pockets.
  • the fluid channel can communicate with the pressure side of the pump be connected, so that continuously lubricating oil between Planetary and storage bag is fed to an improved Lubricant structure to ensure.
  • all moving parts of the gear rotor set in particular the outer rotor and / or the Planetary gears and / or the inner rotor on at least one Front side of a circumferential bridge on.
  • This circular walkway serves as a seal within the housing, in which the Gear rotor set is added.
  • Such movable parts have a sealing surface on their end faces on, which extends over the entire surface.
  • the inventive seal by means of the circumferential ridge has to the advantage that occurring in the known seals high friction forces are greatly reduced and so the Gear rotor set lighter and therefore more efficient.
  • the circumferential ridge has a width which the Represents optimum between sealing effect and friction force.
  • the invention relates to a process for the preparation a toothed rotor set, this being used in a molding process, preferably by means of powder metallurgy Method, plastic injection molding, extrusion, die casting, in particular Alu réelleguß, and punching process is produced.
  • a complex toothing as the inventive Has Zahnahnungsrotorsatz is by means of these methods simple and inexpensive to produce.
  • a production by machining, for example by grinding, milling, Bumping and sawing, which is known to be commonplace Gears can be used in the invention find no application, because the toothing too complicated is trained.
  • the toothed rotor set in a pump in particular a Lubricating oil pump for combustion engines, transmissions, hydraulic power units and high pressure cleaning equipment used becomes.
  • FIG. 1 shows a toothed rotor set 0.1 according to the state the technology, consisting of a rotatable outer rotor 0.2 with Storage bags 0.3, in which rotatably mounted planet gears 0.4 are arranged, which form an internal toothing, with a eccentric to the outer rotor 0.2 mounted inner rotor 0.5 with approximately star-shaped outer contour, with an outer fine toothing 0.6 is provided, wherein the star-shaped Au texveriereung one tooth less than the internal toothing.
  • the gear rotor set 0.1 has seven planet gears 0.4 on.
  • FIG. 2 shows a toothed rotor set 1 according to the invention for a pump or a motor, consisting of a rotatable External rotor 2, which is an approximately star-shaped bore. 3 with a réellefeinveriereung 4 and one in the bore. 3 eccentrically mounted inner rotor 5, the bearing pockets 6 for Planet wheels 7, the planet gears 7 have a Fine toothing on with them in the fine toothing of the outer rotor 2 roll, the planetary gears 7 a toothing 8, which forms an outer toothing, wherein the External teeth one tooth less than the internal teeth 4 of the outer rotor 2.
  • the Veriereungsrotorsatz 1 points a suction region 9 and a pressure region 10 and displacement chambers 11 on. Compared to that shown in Fig. 1 teeingungsrotorsatz 0.1 according to the prior art, be for the gear rotor set 1 according to the invention only 6 planet wheels 7 needed so that less friction occurs.
  • a drive torque M1 acts via a drive shaft 12 the inner rotor 5. This causes an impact force F2 on the Storage pocket 6 of the inner rotor 5 on the planet 7.
  • the Impact force F3 in the planetary gear 7 is divided into two components, the radial force F4 and the torque M4.
  • the impact force F3 acts through the center of the toothed planetary gear 7 the toothed outer rotor 2 and puts this in rotation.
  • the torque M4 the toothed planetary gear 7 in Rotation offset.
  • the planet 7 transmits above all the Impact force F3 and learns by a friction in the bearing pocket caused low friction torque MR.
  • the toothed rotor 1 according to the invention can be used as a pump for Pressure generation can be used, in which the inner rotor. 5 is driven via a drive shaft 12.
  • the toothed rotor set 1 according to the invention can also be used as a motor be used, in which the pressure area 10 with pressure is acted upon, so that the inner rotor 5 is set in rotation and drives the drive shaft 12.
  • FIG. 2a shows the toothed rotor set 1 in a second working position. Here is the sealing effect of the fine toothing very clearly visible.
  • FIG. 2b shows a plan view of the toothed rotor set 1, wherein both a suction side 14 and a pressure side 15th are shown.
  • the suction side 14 opens an inlet opening 16 a, for example, laterally as a hole in the Be formed toothing rotor set receiving housing can.
  • an outlet opening opens into the pressure side 15 17 one.
  • the diameter of the outlet opening 17 may be less than that of the inlet opening 16, since in the latter a higher Flow rate is given.
  • Fig. 3 shows a variant I of the toothing according to the invention according to the detail "X" in Fig. 2.
  • the shown in Fig. 2 large impact force F3 and the only small friction torque MR need be transmitted.
  • this toothing are tooth head 18th and tooth root 19 in the rolling process, d. H. the rolling of the toothed planetary gear 7 on the toothed outer rotor curve 2 included.
  • the surface portions of the teeth were chosen so that they correspond to the distribution of forces.
  • the tooth tip 18.1 of the toothed outer rotor 2 is calculated in such a way that that he exactly meshed with the tooth base 19.2 of the tooth Planet gear 7 applies, and ensures a smooth unrolling. Conversely, the tooth tip engages 18.2 of the toothed Planetary gear 7 in the tooth root 19.1 of the toothed outer rotor 2 on. It comes through the convex tooth head 18.1 of the toothed outer rotor 2 and the concave executed Tooth 19.2 of the toothed planetary gear 7 to a Touchpad and not to a touch line. By This pairing therefore greatly reduces the Hertzian pressure.
  • Fig. 4 shows a second position of the toothing according to the invention.
  • the size of the Flattening 22 depends on the field of application of the toothed rotor 1 from. At low speeds and high pressures must be a strong Flattening 22 are provided. At a high speed and low pressures, a moderate flattening 22 is sufficient, to build up a continuous lubricating film.
  • a cycloid 23 was used which was the lubricating film construction more favorable than a simple transition radius.
  • FIG. 5 shows a third variant of the toothing according to the invention, the tooth flanks 21 of the toothed outer rotor 2 and the toothed planet gears 7 by an involute 24th be formed.
  • the tooth head 18 of the planetary gear 7 is against it formed as a cycloid 25.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Supercharger (AREA)
  • Retarders (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Centrifugal Separators (AREA)
  • Gears, Cams (AREA)
EP01907521A 2000-03-05 2001-02-10 Inverser verzahnungsrotorsatz Expired - Lifetime EP1261806B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10010170A DE10010170A1 (de) 2000-03-05 2000-03-05 Inverser Verzahnungsrotorsatz
DE10010170 2000-03-05
PCT/EP2001/001481 WO2001066949A1 (de) 2000-03-05 2001-02-10 Inverser verzahnungsrotorsatz

Publications (2)

Publication Number Publication Date
EP1261806A1 EP1261806A1 (de) 2002-12-04
EP1261806B1 true EP1261806B1 (de) 2005-11-23

Family

ID=7633239

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01907521A Expired - Lifetime EP1261806B1 (de) 2000-03-05 2001-02-10 Inverser verzahnungsrotorsatz

Country Status (12)

Country Link
US (1) US6695603B2 (ja)
EP (1) EP1261806B1 (ja)
JP (1) JP3977081B2 (ja)
KR (1) KR100481555B1 (ja)
CN (1) CN1188599C (ja)
AT (1) ATE310905T1 (ja)
AU (1) AU2001235465A1 (ja)
BR (1) BR0108961B1 (ja)
CA (1) CA2401430C (ja)
DE (2) DE10010170A1 (ja)
MX (1) MXPA02008115A (ja)
WO (1) WO2001066949A1 (ja)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4557514B2 (ja) 2003-07-15 2010-10-06 住友電工焼結合金株式会社 内接歯車式ポンプ及びそのポンプのインナーロータ
DE10349030B4 (de) * 2003-10-13 2005-10-20 Gkn Driveline Int Gmbh Axialverstellvorrichtung
DE102004047817B3 (de) 2004-09-29 2005-12-08 Gkn Sinter Metals Gmbh Nockenwellenversteller für eine Verbrennungskraftmaschine
JP4608365B2 (ja) * 2005-01-13 2011-01-12 住友電工焼結合金株式会社 内接歯車ポンプの歯形創生方法及び内接歯車
JP4369940B2 (ja) * 2006-07-12 2009-11-25 アイシン・エーアイ株式会社 回転軸オイルシール部の潤滑構造
US7670122B2 (en) * 2006-08-15 2010-03-02 Arvinmeritor Technology, Llc Gerotor pump
DE102008054753A1 (de) * 2008-12-16 2010-06-17 Robert Bosch Gmbh Innenzahnradpumpe
DE102008054761A1 (de) 2008-12-16 2010-06-17 Robert Bosch Gmbh Zahnradanordnung
US10145454B2 (en) * 2015-07-25 2018-12-04 Wieslaw Julian Oledzki Sliding friction-free gear
CN111764998B (zh) * 2020-07-18 2022-05-24 刘少林 多转子纯滚动内燃机
DE102022201642A1 (de) * 2022-02-17 2023-08-17 Vitesco Technologies GmbH Gerotor-Pumpenstufe, Förderpumpe, Fahrzeug sowie Verfahren zur Herstellung der Gerotor-Pumpenstufe, der Förderpumpe und des Fahrzeugs

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE288340C (ja) *
US3623829A (en) * 1969-11-12 1971-11-30 Nichols Co W H Internal gear set
US3619089A (en) * 1970-03-13 1971-11-09 Automatic Radio Mfg Co Fluid-pressure device
US3979167A (en) * 1975-01-27 1976-09-07 Grove Leslie H Internal gear set having roller teeth
DE2922921A1 (de) * 1978-06-07 1979-12-20 Nichols Co W H Innen-gerotor und verfahren zu seinem betrieb
DE3144572C2 (de) * 1981-11-10 1986-02-06 Hans-Joachim Prof. Dr.-Ing. 6750 Kaiserslautern Winkler Drehkolbenmaschine mit verzahntem Innen- und Außenläufer
DE4311166C2 (de) * 1993-04-05 1995-01-12 Danfoss As Hydraulische Maschine
DE19646359C2 (de) 1996-11-09 2001-12-06 Gkn Sinter Metals Gmbh Schmierölpumpe mit einem Verzahnungsrotorsatz
DE19922792A1 (de) * 1999-05-18 2000-11-23 Gkn Sinter Metals Holding Gmbh Verzahnungsrotorsatz

Also Published As

Publication number Publication date
CN1188599C (zh) 2005-02-09
DE50108167D1 (de) 2005-12-29
EP1261806A1 (de) 2002-12-04
US6695603B2 (en) 2004-02-24
ATE310905T1 (de) 2005-12-15
BR0108961B1 (pt) 2010-11-30
KR100481555B1 (ko) 2005-04-07
JP3977081B2 (ja) 2007-09-19
DE10010170A1 (de) 2001-09-06
WO2001066949A1 (de) 2001-09-13
KR20020091106A (ko) 2002-12-05
CN1411537A (zh) 2003-04-16
AU2001235465A1 (en) 2001-09-17
JP2003526050A (ja) 2003-09-02
CA2401430C (en) 2005-12-20
MXPA02008115A (es) 2003-12-11
CA2401430A1 (en) 2001-09-13
US20030072665A1 (en) 2003-04-17
BR0108961A (pt) 2002-12-24

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